JP2003254233A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor in which rotational vibration and vibration caused by imbalance of a converting mechanism around an axis line of a rotary shaft is reduced, and a size and weight are also reduced. <P>SOLUTION: A swash plate 20 is integrally and rotatably connected to a rotation supporting body 19 fixed to the rotary shaft 16 via a hinge mechanism 21 provided on a top dead point side around the axis line of the rotary shaft 16. A pulley 17 integrally and rotatably fixed at a front end part of the rotary shaft 16 is provided with a plurality of rollers 47 separated by prescribed intervals from a rotation center axis line of the pulley 17 and performing pendulum motions with an axis line parallel to the axis line as a center. In each of the rollers 47, mass distribution (number) is set to be larger on a bottom dead point side than that on the top dead point side. As a result, imbalance of the converting mechanism due to providing of the hinge mechanism 21 on the top dead point side is cancelled by the rollers 47 whose mass distribution on the bottom dead point side is set to be larger than that on the top dead point side. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor provided with a conversion mechanism for converting rotational movement of a rotary shaft into compression movement of a compression member in a compression mechanism.

[0002]

2. Description of the Related Art As a compressor of this type, for example, the configuration disclosed in Japanese Patent Laid-Open No. 7-158560 is known. In this configuration, the rotational motion of the drive shaft (rotary shaft) is converted into the swinging motion of the swash plate that is connected to the rotor (rotary support) that is synchronously rotatably supported by the drive shaft via the hinge mechanism. It The swinging motion of the swash plate is converted into a reciprocating motion of a piston (compressing member) for compressing the refrigerant. That is, in this configuration, the rotor, the hinge mechanism, the swash plate, and the like constitute a conversion mechanism for converting the rotational movement of the drive shaft into the compression movement of the piston.

In this conversion mechanism, the hinge mechanism is provided on the top dead center side around the axis of the drive shaft. As a result, the conversion mechanism is configured to have a biased weight around the axis of the drive shaft. This uneven weight can be a factor in generating vibration when the drive shaft rotates.

In this structure, a counterweight is mounted on the swash plate at the bottom dead center side around the axis of the drive shaft. With this counterweight, it becomes possible to cancel the bias of the conversion mechanism.

As a structure for canceling the unbalanced weight of the conversion mechanism, for example, a counterweight is provided on the bottom dead center side of the rotor to balance the mass of the conversion mechanism around the axis of the drive shaft. It is possible.

[0006]

However, in order to sufficiently cancel the uneven load in the above-mentioned structure, it is necessary to provide the counter weight having a size or a mass that can cope with the uneven load, which is necessary for the compressor. It becomes a factor of increasing size and weight.

Further, in the structure disclosed in the above publication, no consideration is given to suppression of rotational vibration of the drive shaft and the like. An object of the present invention is to provide a compressor capable of reducing rotational vibrations and vibrations due to an unbalanced weight of a conversion mechanism around an axis of a rotary shaft, and at the same time being capable of being reduced in size and weight.

[0008]

In order to solve the above problems, in the invention described in claim 1, the compressor converts the rotational movement of the rotary shaft into the compression movement of the compression member in the compression mechanism. And a rotating body integrally rotatable with the rotating shaft. The rotating body is provided with a mass body. The mass body performs a pendulum motion about an axis line that passes through a point that is separated from the rotation center axis line of the rotating body by a predetermined distance and that is substantially parallel to the rotation center axis line. In the rotating body, the mass body is provided so as to cancel the bias of the conversion mechanism around the axis of the rotating shaft.

According to the present invention, the rotational vibration of the rotating body and the rotating shaft is suppressed by the pendulum motion of the mass body accompanying the rotation of the rotating body. The mass body is provided in the rotary body so as to cancel the bias of the conversion mechanism around the axis of the rotary shaft. Therefore, it is possible to reduce the vibration caused by the unbalanced weight of the conversion mechanism. Further, it is possible to reduce the size and weight of the counter weight provided in the conversion mechanism or the like in order to cancel the uneven weight. Alternatively, it is not necessary to specially provide the counter weight. As a result, it is possible to reduce the size and weight of the compressor itself.

According to a second aspect of the invention, in the first aspect of the invention, a plurality of the mass bodies are provided. The mass bodies are arranged at non-uniform intervals in the circumferential direction of the rotating body.

According to the present invention, by disposing a plurality of mass bodies at non-uniform intervals in the circumferential direction of the rotating body, it becomes possible to cancel the bias of the conversion mechanism around the axis of the rotating shaft.

According to a third aspect of the invention, in the invention of the first or second aspect, a plurality of the mass bodies are provided. A part of the mass bodies has a mass different from other mass bodies.

According to the present invention, it is possible to cancel the bias of the conversion mechanism around the axis of the rotating shaft by making the mass of one of the plurality of mass bodies different from that of the other mass body. Become.

According to a fourth aspect of the invention, in the third aspect of the invention, a part of the mass bodies is different in volume from the other mass bodies. According to the present invention, by making the volume of a part of the plurality of mass bodies different from that of another mass body, the mass per one of the mass bodies can be made different from that of the other mass body.

According to a fifth aspect of the present invention, in the fourth aspect of the present invention, the mass body is a circle arranged so as to be movable along a guide surface formed in the rotating body and having an arcuate cross section. It is a columnar roller. Some of the mass bodies differ in diameter from the other mass bodies.

According to the present invention, by making the diameter of a part of the plurality of cylindrical mass bodies different from that of the other mass bodies, the mass per one of the mass bodies is different from that of the other mass bodies. Can be different. Further, due to the difference in the diameter, it becomes possible to deal with a plurality of rotational order components in the rotational vibration.

According to a sixth aspect of the present invention, in the fourth or fifth aspect of the present invention, the mass body is movably arranged along a guide surface formed in the rotating body and having an arcuate cross section. It is a cylindrical roller. A part of the mass body has an axial length different from that of the other mass bodies.

According to the present invention, by making the axial length of a part of the plurality of cylindrical mass bodies different from that of the other mass bodies, the mass per one of the mass bodies can be changed. Can be different from the others.

According to the invention described in claim 7, claims 3 to 6 are provided.
In the invention described in any one of 1 above, a part of the mass body is made of a material having a density different from that of the other mass bodies.

According to the present invention, by making the material of a part of the plurality of mass bodies different from the density of the other mass bodies, the mass per one of the mass bodies can be changed to the other mass body. Can be different.

In the invention described in claim 8, claims 1 to 7 are provided.
In the invention described in any one of 1, the plurality of mass bodies are provided. A part of the mass body is different from the other mass bodies in the distance between the pendulum motion center and the rotation center axis of the rotating body.

According to the present invention, it is possible to deal with a plurality of rotational order components in the rotational vibration due to the difference in the intervals. Further, in the mass body having the larger spacing, it becomes easier to secure a larger number of mass bodies arranged in the circumferential direction of the rotating body and a larger space for the mass body than in the mass body having the smaller spacing. That is, it becomes easy to make the mass distribution non-uniform around the axis of the rotation axis of the mass body.

In the invention described in claim 9, claims 1 to 8 are provided.
In the invention described in any one of 1 above, the compression mechanism is a piston type compression mechanism including a plurality of pistons as the compression members around the axis of the rotation shaft. The conversion mechanism includes a rotation support body that is integrally rotatable with the rotation shaft. The conversion mechanism includes a swash plate that is integrally rotatably connected to the rotation support body via a hinge mechanism that is provided on the top dead center side around the axis of the rotation shaft, and between the piston and the swash plate. And a shoe interposed therebetween. The swash plate is supported by the hinge mechanism so as to be tiltable with respect to the axial direction of the rotary shaft. The mass distribution of the mass body is set to be larger on the bottom dead center side than on the top dead center side.

According to the present invention, the stroke of the piston, that is, the discharge capacity per one rotation of the rotating shaft of the compressor can be changed by tilting the swash plate. In this configuration, the bias of the conversion mechanism due to the hinge mechanism provided on the top dead center side around the axis of the rotation axis is such that the mass distribution on the bottom dead center side is set to be larger than that on the top dead center side. Can be countered by the body. That is, it is possible to reduce the vibration caused by the unbalanced weight of the conversion mechanism.

The side where the piston is located at the top dead center around the axis of the rotating shaft is the top dead center side around the axis of the rotating shaft, and the side where the piston is located at the bottom dead center is the axis of the rotating shaft. It is the bottom dead center side in the surrounding area.

According to a tenth aspect of the invention, in the invention of the ninth aspect, a plurality of the mass bodies are provided. The mass body is set such that the number of the mass bodies on the bottom dead center side is larger than that on the top dead center side in the rotating body.

According to the present invention, since the mass body is provided more on the bottom dead center side than on the top dead center side in the rotating body, the mass distribution of the mass body on the bottom dead center side is larger than that on the top dead center side. It becomes easy to make it large.

According to an eleventh aspect of the invention, in the invention of the ninth or tenth aspect, a plurality of the mass bodies are provided. The mass per one of the mass bodies arranged on the bottom dead center side is set to be larger than the mass per one mass body arranged on the top dead center side.

According to the present invention, the mass per mass of the bottom dead center side is set to be larger than the mass per mass of the top dead center side, so that the mass dead center side of the mass dead center side It becomes easy to make the mass distribution larger than that at the top dead center side.

According to the invention described in claim 12, claims 9 to 9 are provided.
In the invention described in any one of 11 above, a plurality of the mass bodies are provided. The corresponding rotation order component of the mass body arranged on the bottom dead center side is set to a higher order than the corresponding rotation order component of the mass body arranged on the top dead center side.

This configuration is suitable for making the mass distribution of the mass body on the bottom dead center side around the axis of the rotation axis larger than that on the top dead center side.

[0032]

BEST MODE FOR CARRYING OUT THE INVENTION (First Embodiment) An embodiment of the present invention will be described below with reference to FIGS. In addition,
In FIG. 1, the left side of the drawing is the front of the compressor and the right side is the rear.

As shown in FIG. 1, the compressor C is joined and fixed to a cylinder block 11, a front housing 12 joined and fixed to the front end thereof, and a valve housing 13 to the rear end of the cylinder block 11. And a rear housing 14. The cylinder block 11, the front housing 12, the valve forming body 13, and the rear housing 14 form a housing of the compressor C.

A crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing 12. A rotary shaft 16 arranged so as to penetrate the crank chamber 15 is rotatably supported in the housing.

The front end portion of the rotary shaft 16 is arranged so as to penetrate the front wall of the front housing 12 and project to the outside. A front end portion of the rotary shaft 16 has a pulley 17 as a rotating body described below and a belt 1 mounted on the pulley 17.
8 is operatively connected to a vehicle engine E as an external drive source.

A rotary support 19 is fixed to the rotary shaft 16 in the crank chamber 15 so as to be integrally rotatable. A swash plate 20 as a cam plate is housed in the crank chamber 15. The swash plate 20 is supported so as to be slidable and tiltable with respect to the rotary shaft 16. The swash plate 20
It is operatively connected to the rotary support 19 via a hinge mechanism 21 described later.

The hinge mechanism 21 includes a support arm 19A protruding from the rear surface side of the rotary support 19 toward the rear side,
The swash plate 20 includes a connecting pin 20A protruding from the front side toward the front side. A connecting hole 19B is formed at the tip side of the support arm 19A, and a substantially spherical connecting portion 20B formed at the tip of the connecting pin 20A is slidably fitted into the connecting hole 19B.

The swash plate 20 can rotate integrally with the rotary support 19 and the rotary shaft 16 by the above-mentioned operation connection with the rotary support 19 via the hinge mechanism 21 and the support of the rotary shaft 16, and It is possible to tilt with respect to the rotating shaft 16 while the sliding movement of 16 in the axial direction is accompanied.

The swash plate 20 has a minimum inclination of the swash plate 20 due to a locking ring 22 fixed to the rotating shaft 16 and a spring 23 arranged between the locking ring 22 and the swash plate 20. The angle is specified. The minimum tilt angle of the swash plate 20 refers to the tilt angle when the angle between the swash plate 20 and the axial direction of the rotary shaft 16 is closest to 90 °.

A plurality of cylinder bores 24 (only one is shown in FIG. 1) are formed through the cylinder block 11 so as to extend along the axial direction of the rotary shaft 16. A single-headed piston 25 (compression member) is reciprocally housed in the cylinder bore 24. The front and rear openings of the cylinder bore 24 are closed by the valve forming body 13 and the piston 25, and a compression chamber whose volume changes according to the reciprocating movement of the piston 25 is defined in the cylinder bore 24. Each piston 25 is moored to the outer peripheral portion of the swash plate 20 via a shoe 26. As a result, the rotational movement of the rotary shaft 16 causes the rotary support 19, the swash plate 20, and the shoe 2 to rotate.
Reciprocating linear movement of piston 25 (compression movement) via 6 etc.
It is designed to be converted to.

The rotary shaft 16, the rotary support 19, the swash plate 20, the hinge mechanism 21, the piston 25 and the shoe 26 constitute a piston type compression mechanism. Also,
Among these, the rotary support 19, the swash plate 20, the hinge mechanism 21, and the shoe 26 constitute a conversion mechanism for converting the rotational movement of the rotary shaft 16 into the compression movement of the piston 25.

The rear housing 14 has a suction chamber 27 and a discharge chamber 28 defined therein. Suction chamber 27
The front side of the discharge chamber 28 is closed by the valve forming body 13. The refrigerant gas (fluid) in the suction chamber 27 moves to the cylinder bore 24 (compression chamber) through the suction port 29 and the suction valve 30 formed in the valve body 13 by the movement of each piston 25 from the rear side to the front side. be introduced. The low-pressure refrigerant gas introduced into the cylinder bore 24 is compressed to a predetermined pressure by the movement of the piston 25 from the front side to the rear side, and passes through the discharge port 31 and the discharge valve 32 formed in the valve forming body 13. It is introduced into the discharge chamber 28.

The suction chamber 27 and the discharge chamber 28 are connected by an external refrigerant circuit (not shown). The refrigerant discharged from the discharge chamber 28 is introduced into the external refrigerant circuit. In this external refrigerant circuit, heat exchange using the refrigerant is performed.
The refrigerant discharged from the external refrigerant circuit is introduced into the suction chamber 27, sucked into the cylinder bore 24, and subjected to the compression action again.

A bleed passage 33 is provided in the housing to connect the crank chamber 15 and the suction chamber 27.
Further, the discharge chamber 28 and the crank chamber 1 are provided in the housing.
An air supply passage 34 that communicates with the fuel cell 5 is provided. The opening of the air supply passage 34 can be adjusted by a control valve 35 provided on the air supply passage 34 (on the way of the air supply passage 34).

By adjusting the opening of the control valve 35, the balance between the amount of high-pressure refrigerant gas introduced into the crank chamber 15 through the air supply passage 34 and the amount of gas discharged from the crank chamber 15 through the extraction passage 33 is balanced. Is controlled, and the crank pressure (internal pressure of the crank chamber 15) Pc is determined. According to the change of the crank pressure Pc, the difference between the crank pressure Pc via the piston 25 and the internal pressure of the compression chamber is changed, and the inclination angle of the swash plate 20 is changed. As a result, the stroke of the piston 25, that is,
The discharge capacity per one rotation of the rotary shaft 16 is adjusted.

Here, the state in which the volume of the compression chamber is smallest during one rotation of the rotary shaft 16 is the piston 2
5 is located at the top dead center, and the state in which the volume of the compression chamber is the largest is the state where the piston 25 is located at the bottom dead center. The side where the piston 25 is located at the top dead center around the axis of the rotary shaft 16 is called the top dead center side around the axis of the rotary shaft 16, and the side where the piston 25 is located at the bottom dead center is It is assumed to be the bottom dead center side around the axis of the rotary shaft 16.

In this embodiment, the hinge mechanism 21 is used.
Are provided on the top dead center side around the axis of the rotating shaft 16 (upper side of the rotating shaft 16 in FIG. 1). That is, the support arm 19A and the connecting pin 20A are provided on the rotary support 19 and the swash plate 20, respectively, on the top dead center side around the axis of the rotary shaft 16.

In the rotary support 19, on the side of the bottom dead center around the axis of the rotary shaft 16, the rotary support 1 around the axis of the rotary shaft 16 due to the mass of the support arm 19A.
A counterweight portion 19C is provided to reduce the weight of the counterweight 9. Further, in the swash plate 20, the rotary shaft 16
A counterweight portion 20C is provided on the side of the bottom dead center around the axis of No. 1 to reduce the bias of the swash plate 20 around the axis of the rotating shaft 16 due to the mass of the connecting pin 20A.

As shown in FIGS. 1 and 2 (b), the pulley 17 is rotated by a bearing 41 arranged on the outer peripheral surface of a support cylinder portion 40 provided on the front outer wall surface of the front housing 12. It is fixed to the rotary shaft 16 so as to be integrally rotatable while being supported in a possible manner.

As shown in FIGS. 1 and 2, the pulley 17
Includes a pulley body 42 made of resin. The pulley body 42 has a boss portion 4 attached to the outer ring of the bearing 41.
3 and a belt hooking portion 44 on which the belt 18 is hooked. Six recesses 45 serving as rolling guides are formed in a portion of the pulley 17 between the boss portion 43 and the belt hooking portion 44 (only one is shown in FIG. 1).

The recesses 45 are arranged at uniform intervals in the circumferential direction of the pulley 17. Also, the six recesses 45
Of these, three recesses 45 (recesses 45A, 45B, 45
C) is the remaining three recesses 45 (recesses 45D, 45E, 45F) on the top dead center side around the axis of the rotating shaft 16.
Are arranged on the bottom dead center side around the axis.
As shown in FIG. 2A, the recesses 45A, 45B, 45C
Are arranged in the clockwise direction from the left side of the drawing on the top dead center side around the axis.
Further, the recesses 45D, 45E, 45F are arranged in the clockwise direction from the right side of the drawing on the bottom dead center side around the axis, respectively.

Each of the recesses 45 has a rolling guide surface 4 having a circular arc-shaped cross section on a plane orthogonal to the rotation center axis of the pulley 17.
6 (guide surface) is formed. The rolling guide surface 46 has a predetermined distance from the rotation center axis of the pulley 17 (this distance is R ₁
And a part of the inner peripheral surface of the virtual cylinder having a radius r ₁ centered on an axis parallel to the rotation center axis.

In each of the four recesses 45 out of the six, one roller 47 as a mass body (the diameter of each roller 47 is d ₁ and the mass of each roller 47 is m ₁ ) is accommodated one by one. Has been done. That is, the roller 47 includes three recesses 45 (recesses 45D, 4D) on the bottom dead center side around the axis of the rotating shaft 16.
5E, 45F) and one recess 45 (recess 45B) on the top dead center side around the axis. The rollers 47 are made of a metal (iron in the present embodiment) of the same material (same density), and are formed in a cylindrical shape having the same shape and the same size, so that they have the same mass.

Each roller 47 is accommodated in each recess 45 along the rolling guide surface 46 so as to be rollable in the circumferential direction of the rolling guide surface 46. Each roller 47 is prevented from rolling down to the outside of each recess 45 by an annular resin cover 48 fixed to the opening side (front side) of each recess 45 by screwing.

When the compressor C is driven by the vehicle engine E, that is, when the rotary shaft 16 rotates, each roller 47 is brought into contact with the rolling guide surface 46 by a centrifugal force ( 1 and 2). In this state, when torque fluctuations due to torsional vibrations (rotational vibrations) of the rotating shaft 16 occur, the rollers 47 in the recesses 45 respectively follow the rolling guide surfaces 46 (the rolling guide surfaces 46). Reciprocating movement is started. In other words, (the center of gravity of) each roller 47 performs a pendulum motion centered on the central axis of the inner peripheral surface of the virtual cylinder whose part is constituted by the rolling guide surface 46. Therefore, each roller 47 acts as a centrifugal pendulum when the compressor C is driven by the vehicle engine E. In the present embodiment, the torque fluctuation (rotational vibration) is
In order to suppress it by the pendulum movement of the roller 47, the roller 4
The arrangement position, size, mass, etc. of the No. 7 pulley 17 are set.

Here, the roller 4 acting as a centrifugal pendulum
The above-mentioned settings for No. 7 will be described. Roll 47
Is the torque fluctuation (the fluctuation width of the torque fluctuation) at a frequency equal to the natural frequency of the roller (centrifugal pendulum) 47.
It acts to hold down. Therefore, by setting the arrangement position, size, mass and the like of the roller 47 on the pulley 17 so that the natural frequency of the roller 47 becomes equal to the peak frequency of the torque fluctuation, the torque fluctuation of this peak can be obtained. It becomes possible to effectively suppress the effect of the torque fluctuation as a whole. The peak of the torque fluctuation indicates the peak of the fluctuation width of the torque fluctuation, that is, the rotation order component.

The frequency of the torque fluctuation and the natural frequency of the roller 47 are proportional to the angular velocity ω ₁ of the rotating shaft 16 which is correlated with the rotating speed of the rotating shaft 16. Moreover, the frequency of the torque fluctuation when the peak of the torque fluctuation of the compressor C appears, the rotational speed per unit of the rotary shaft 16 time (= ω _1/2
π) and the number of cylinders (the number of cylinder bores 24) N (ω ₁
/ 2π) · N. In the compressor C, the nth (n is a natural number) largest frequency of the torque fluctuation peaks has a product n · (ω ₁ / 2π).
-It has been found through experiments that the value tends to be the same as N.

On the other hand, the natural frequency of the roller 47 is 1
6 rotations per unit time (= ω ₁/ 2π) and the ratio R
It is given by the product of the square root value of / r. In addition, here
R is a pulley 17 (a mass body that performs pendulum motion is installed
Rotation center axis of the rotating body) and the roller 47 (mass body)
It is the distance from the central axis of the pendulum motion, and r is the value of the roller 47.
The distance between the center axis of the pendulum motion and the center of gravity of the roller 47.
It

Therefore, the product of the square root values of the ratio R / r is n.
By setting it equal to the value of N, it is possible to match the n-th largest peak frequency of the torque fluctuation with the natural frequency of the roller 47. This makes it possible to suppress the torque fluctuation at the frequency of the nth largest peak. Accordingly, in this embodiment, in order to suppress the peak of the torque fluctuation, the magnitudes of R and r are set so that the square root value of the ratio R / r becomes equal to the value of n · N.

In order to efficiently suppress the torque fluctuation by the pendulum motion of the roller 47, the torque T about the rotation center axis of the pulley 17 which is acted by the roller 47 is exerted.
Needs to be made equal in magnitude to the fluctuation width of the torque fluctuation to be opposed. The torque T in a state in which the peak frequency of the torque fluctuation and the natural frequency of the roller 47 match
It has been found that the magnitude of is given by:

T = m · (ω _a ) ² · (R + r) · R · φ where m is the total mass of all rollers 47 (m = 4 · m ₁ ), and ω _a is the minute swing angle φ. Is the average angular velocity of the roller 47 that performs the pendulum motion at.

In the present embodiment, the central axis of the inner peripheral surface of the virtual cylinder, a part of which is formed by the rolling guide surface 46, is the central axis of the pendulum motion of the roller 47 (the fulcrum of the pendulum motion is This is on the central axis). That is, the distance R ₁ between the rotation center axis of the pulley 17 and the center axis of the virtual cylinder inner peripheral surface corresponds to the distance R.

The distance between the center axis of the pendulum motion of the roller 47 and the center of gravity of the roller 47 is obtained by subtracting half the diameter d ₁ of the roller 47 from the radius r ₁ of the inner peripheral surface of the virtual cylinder. Is equal to the number. That is, the difference {r ₁ − (d ₁ /
2)} corresponds to the distance r.

[0064] That is, in this embodiment, in order to stifle peak of the torque fluctuation corresponds to the square root value of the ratio R / r, the ratio _{R 1 / {r 1 - (} d 1/2)} square value of The magnitudes of R ₁ , r ₁ and d ₁ are set so that is equal to the value of n · N.

In the pendulum motion described above, various settings are made with the roller 47 as a mass point where the mass is concentrated on its center of gravity. In addition, the roller 47 in the pendulum motion
Since the swing angle φ of the rotary shaft 16 is very small, the rollers 47 are
It is located almost at the center in the circumferential direction.

Next, the operation of the compressor C configured as described above will be described. Vehicle engine E to pulley 17
When power is supplied to the rotary shaft 16 via the
The swash plate 20 rotates together with 6. As the swash plate 20 rotates, each piston 25 is reciprocated with a stroke corresponding to the inclination angle of the swash plate 20, and the refrigerant suction, compression, and discharge are sequentially repeated in each cylinder bore 24.

When the opening of the control valve 35 becomes small,
From the discharge chamber 28 through the air supply passage 34 to the crank chamber 15
The amount of high-pressure refrigerant gas supplied to the crankshaft is reduced, the crank pressure Pc is reduced, and the inclination angle of the swash plate 20 is increased.
The discharge capacity of the compressor C increases. Conversely, when the opening degree of the control valve 35 increases, the amount of high-pressure refrigerant gas supplied from the discharge chamber 28 to the crank chamber 15 via the air supply passage 34 increases, the crank pressure Pc increases, and the swash plate increases. The inclination angle of 20 becomes small, and the discharge capacity of the compressor C becomes small.

When the rotary shaft 16 rotates, the reaction force due to the compression reaction of the refrigerant or the reciprocal motion of the piston 25 is transmitted to the rotary shaft 16 through the swash plate 20, the hinge mechanism 21, etc. Torsional vibration (rotational vibration) is generated in 16. This torsional vibration causes torque fluctuations. The torque fluctuation causes resonance between the compressor C itself and external devices operatively connected to the pulley 17 via the belt 18 (vehicle engine E, auxiliary machinery, etc.) and the compressor C. It is a thing.

When the torque fluctuation occurs, the pulley 17
The roller 47 provided at the position starts the pendulum movement. The torque applied around the rotation center axis of the pulley 17 by this pendulum motion acts to suppress the torque fluctuation.

Further, due to the large number of rollers 47 arranged on the bottom dead center side around the axis of the rotary shaft 16 rather than the top dead center side, the hinge mechanism 21 causes the hinge mechanism 21 to move to the top dead center side around the axis. It acts so as to cancel out the bias of the conversion mechanism caused by being provided in the.

In this embodiment, the following effects can be obtained. (1) The pulley 17 is provided with a roller 47 which is separated from the rotation center axis of the pulley 17 by a predetermined distance R ₁ and performs a pendulum motion about an axis parallel to the rotation center axis. According to this, the rotational vibration (the torque fluctuation) is suppressed by the pendulum motion of the roller 47, and the compressor C,
Resonance generated between the vehicle engine E and the compressor C, which are operatively connected to the pulley body 42 via the belt 18, are suppressed.

(2) Since the structure (roller 47 etc.) for suppressing the rotational vibration is provided on the pulley 17, it is necessary to specially provide the means for suppressing the rotational vibration in the housing of the compressor C. Disappear. That is, the housing of the compressor C becomes small. Further, by changing the structure of the pulley 17 without changing the structures of the housing and the compression mechanism, it is possible to change (the order of) the rotational order component and the magnitude of the torque T that can be supported.

(3) In the pulley 17, the roller 47
Are provided so as to cancel the bias of the conversion mechanism around the axis of the rotary shaft 16. Therefore, it is possible to reduce the vibration caused by the unbalanced weight of the conversion mechanism. Further, it becomes possible to reduce the size and weight of the counterweight portions 19C and 20C provided on the rotary support 19 and the swash plate 20. As a result, it is possible to reduce the size and weight of the compressor C itself.

(4) By disposing the rollers 47 in only some of the recesses 45 out of the recesses 45 provided at equal intervals in the circumferential direction of the pulley 17, the plurality of rollers 47 are They were arranged at non-uniform intervals in the circumferential direction. Thereby, the mass distribution of the rollers 47 in the pulley 17 is set so that the bottom dead center side around the axis of the rotary shaft 16 is larger than the top dead center side. Therefore, it becomes possible to cancel the bias of the conversion mechanism around the axis.

(Second Embodiment) In the second embodiment, the configuration of the roller is changed in the first embodiment, and in other points, the configuration is the same as that of the first embodiment. ing. Therefore, the same components as those in the first embodiment are designated by the same reference numerals in the drawings, and duplicated description will be omitted.

As shown in FIG. 3, the pulley 1 according to the present embodiment.
In FIG. 7, rollers (mass bodies) are housed in all (six) recesses 45. That is, in the recesses 45D, 45E, 45F on the bottom dead center side around the axis of the rotary shaft 16, one roller 47 similar to that in the first embodiment is housed. Further, in the recesses 45A, 45B, 45C on the side of the top dead center around the axis, a roller 50 as a mass body having a diameter smaller than that of the roller 47 (the diameter of the roller 50 is d ₂ ) is provided. Each one is housed.

The three rollers 50 are made of the same material (same density) as the rollers 47 (iron in this embodiment). In addition, each roller 50 is formed in a cylindrical shape having the same shape and the same size, so that the rollers 50 have the same mass. That is, each roller 50 has a smaller volume than each roller 47, and therefore has a smaller mass. Therefore, the mass distribution of the rollers (mass bodies) in the pulley 17 is
The bottom dead center side is set to be larger than the top dead center side around the axis of the rotating shaft 16. The bias of the pulley 17 based on this acts so as to cancel the bias of the conversion mechanism due to the hinge mechanism 21 provided on the top dead center side around the axis.

In the present embodiment, the distance between the center axis of the pendulum motion of the roller 50 and the center of gravity of the roller 50 is calculated from the radius r _{1 of the} inner peripheral surface of the imaginary cylinder of the rolling guide surface 46 to the roller 5
It is equal to the number 0 minus half the diameter d ₂ . That is, the difference - the _{{r 1 (d 2/2} )}, corresponding to the distance r. That is, the distance r with respect to the roller 50 is larger than the distance r with respect to the roller 47. That is, the value of the ratio R / r for the roller 50 is smaller than that for the roller 47. Therefore, the roller 50 corresponds to a lower rotational order component than the roller 47. That is, due to the pendulum motion of the roller 50, the torque fluctuation width in the rotational order component lower than the corresponding rotational order component of the roller 47 is suppressed.

In this embodiment, the following effects can be obtained in addition to the same effects as the above (1) to (3). (5) Among the plurality of rollers, the diameter (that is, the volume) of some rollers is made different from that of the other rollers, so that the mass per one of the rollers is made different from that of the other rollers. Thereby, the mass distribution of the rollers in the pulley 17 is
The bottom dead center side is set to be larger than the top dead center side around the axis of. Therefore, it becomes possible to cancel the bias of the conversion mechanism around the axis.

(6) Due to the difference in diameter between the roller 50 and the roller 47, the value of the ratio R / r in each roller 47, 50 can be made different from each other. This makes it possible to deal with a plurality of rotational order components in the rotational vibration.

(7) The corresponding rotation order component of the roller 47 arranged on the bottom dead center side around the axis of the rotation shaft 16 is higher than the corresponding rotation order component of the roller 50 arranged on the top dead center side. It is set next. In this embodiment, the diameter d _{2 of the} roller 50 is set to be smaller than the diameter d _{1 of the} roller 47, so that the value of the distance r with respect to the roller 50 is made larger than the value of the distance r with respect to the roller 47. It is realized by that. In other words, setting the corresponding rotation order component of the roller 47 to a higher order than the corresponding rotation order component of the roller 50 makes the mass distribution of the roller on the bottom dead center side around the axis larger than that on the top dead center side. Suitable to do.

(Third Embodiment) In the third embodiment, the configuration of the recess and the like in the second embodiment is changed, and in other respects, the configuration is similar to that of the second embodiment. Has become. Therefore, the same components as those in the second embodiment are designated by the same reference numerals in the drawings, and duplicated description will be omitted.

As shown in FIG. 4, the pulley 1 of this embodiment
7, the arrangement position and shape of the recesses 45A, 45B, 45C on the top dead center side around the axis of the rotating shaft 16 in the pulley body 42 are the pulley 17 of the second embodiment.
Is different from That is, the radius r ₂ of the inner peripheral surface of the virtual cylinder forming the rolling guide surfaces 46 of the recesses 45A, 45B, 45C is equal to the recess 45D on the bottom dead center side around the axis.
It is set to be smaller than the radius r ₁ of the inner peripheral surface of the virtual cylinder forming the rolling guide surfaces 46 of 45E and 45F. Further, the distance R ₂ (corresponding to the distance R in the ratio R / r) between the center axis of the inner peripheral surface of the virtual cylinder and the rotation center axis of the pulley 17 regarding the recesses 45A, 45B, 45C is equal to the recesses 45D, 45E, It is set smaller than the distance R _{1 for} 45F.

In this embodiment, the recesses 45A, 45
The distance r (the ratio R
Distance r) in the / r is the difference - equivalent to _{{r 2 (d 2/2} )}. In the present embodiment, the recesses 45A, 45B, 45C
Side and the recesses 45D, 45E, 45F side, the ratio R / r
The distances (radius) R ₂ , r ₂ and so on are set so that the values of are equal. That is, both rollers 47, 50 of the present embodiment
Corresponds to only one rotation order component.

In this embodiment, the recess 45 is formed.
The volumes of A, 45B and 45C are concave portions 45D, 45E and 45
Although smaller than the volume of F, the pulley main body 42 is in a state where there is no unbalanced weight around the axis of the rotating shaft 16 due to the thinning around each recess 45. In addition, in the present embodiment, in order to make the distance R ₂ for the recesses 45A, 45B, 45C smaller than the distance R ₁ for the recesses 45D, 45E, 45F, in comparison with the second embodiment, The diameters of the tubular portion 40, the bearing 41, and the boss portion 43 are set to be small.

In this embodiment, the following effects can be obtained in addition to the same effects as the above (1) to (3) and (5). (8) The pulley 17 of this embodiment is configured such that all the recesses 45 accommodate the rollers and all the rollers correspond to one rotation order component. According to this, it becomes relatively easy to secure the total mass of the rollers that can correspond to one rotation order component. Therefore, when suppressing the torque fluctuation in the specific one rotational order component, for example, when the torque fluctuation width of the specific one rotational order component is significantly larger than the other rotational order components, Especially effective for.

(Fourth Embodiment) This fourth embodiment is the same as the first embodiment except that the number of rollers and recesses is changed in the first embodiment. It is configured. Therefore, the same components as those in the first embodiment are designated by the same reference numerals in the drawings, and duplicated description will be omitted.

As shown in FIG. 5, the pulley 1 of this embodiment
In FIG. 7, seven recesses 45 are provided, and rollers 47 are housed in all the recesses 45. The bottom dead center side concave portion 45 around the axis of the rotary shaft 16 is increased by one as compared with the first embodiment. That is,
The recesses 45D, 45 are provided on the bottom dead center side around the axis.
In addition to E and 45F, a recess 45G is provided. The values of the distances (radius) R ₁ and r ₁ with respect to the recess 45G, the diameter d ₁ of the roller 47, and the like are set to be the same as those of the other recesses 45 and the roller 47.

On the bottom dead center side around the axis,
The recesses 45D, 45E, 45F, 45G are arranged at uniform intervals in the circumferential direction of the pulley 17. Pulley 1
When rotating 7, the recesses 45D, 45E, 45F,
The roller 47 accommodated in 45G is not located on the top dead center side around the axis.

In this embodiment, the following effects can be obtained in addition to the same effects as the above (1) to (3) and (8). (9) The number of recesses 45 on the bottom dead center side is increased with respect to the top dead center side around the axis of the rotary shaft 16, and
By accommodating the mass bodies (rollers 47) in all the recesses 45, the plurality of mass bodies (rollers 47) are arranged at non-uniform intervals in the circumferential direction of the pulley 17. Thereby, the mass distribution of the mass body (roller 47) in the pulley 17 is set so that the bottom dead center side is larger than the top dead center side around the axis of the rotating shaft 16. Therefore, it becomes possible to cancel the bias of the conversion mechanism around the axis.

(Fifth Embodiment) The fifth embodiment is different from the third embodiment in that the number and shape of the rollers and the recesses, the arrangement position, etc. are changed. It has the same configuration as that of the embodiment. Therefore,
Constituent parts common to those of the third embodiment are designated by the same reference numerals in the drawings, and redundant description will be omitted.

As shown in FIG. 6, the pulley 1 according to this embodiment.
In FIG. 7, eight concave portions 45 are provided. Recesses 45A, 45 on the top dead center side around the axis of the rotary shaft 16
The configurations of B and 45C are the same as those in the third embodiment. On the other hand, the concave portion 45 on the bottom dead center side around the axis line
Are increased by two compared to the third embodiment. That is, the concave portion 4 is provided on the bottom dead center side around the axis.
In addition to 5D, 45E and 45F, recesses 45G and 45H are provided. On the bottom dead center side around the axis, the recesses 45D, 45E, 45F, 45G and 45H are
The pulleys 17 are arranged at uniform intervals in the circumferential direction.

Recesses 45D, 45E, 45F, 45G, 4
The radius of the inner peripheral surface of the virtual cylinder with respect to 5H is equal to that of the concave portion 45.
It is set to be equal to the radius r ₂ for A, 45B and 45C (hereinafter, recesses 45D, 45E, 45F and 45).
This is also referred to as r ₂ with respect to the radius for G, 45H). Also, the recesses 45D, 45E, 45F, 45G, 4
5H center axis of the virtual cylinder inner peripheral surface and pulley 1
The distance R ₃ (corresponding to the distance R in the ratio R / r) from the rotation center axis line of 7 is set to be larger than the distance R ₂ for the recesses 45A, 45B, 45C.

In this embodiment, all the recesses 45 have recesses 45A, 45B,
The rollers 50 having the same configuration as the rollers 50 accommodated in the 45C are accommodated one by one. In the present embodiment, the distance r (the ratio R /
Distance r) at r, the difference - equivalent to _{{r 2 (d 2/2} )}. Since the distance R ₃ is set larger than the distance R ₂ , the recesses 45D, 45E, 45F, 45G, 4
The value of the ratio R / r with respect to the roller 50 accommodated in 5H is the same as that of the roller 50 accommodated in the recesses 45A, 45B and 45C.
Bigger than that. Therefore, the bottom dead center side roller 50 around the axis of the rotation shaft 16 corresponds to a higher rotation order component than the top dead center side roller 50.

In this embodiment, in addition to the same effects as the above (1) to (3) and (9), the following effects can be obtained. (10) A part of the plurality of rollers 50 is different from the other rollers 50 in the distance between the pendulum movement center and the rotation center axis of the pulley 17. The difference in the distance (the distance R ₃
And the distance R ₂ ), it becomes possible to deal with a plurality of rotational order components in the rotational vibration. Further, in the roller 50 having the larger interval (the roller 50 on the bottom dead center side around the axis of the rotating shaft 16), the roller 50 having the smaller interval is compared to the roller 50 (the roller 50 on the top dead center side around the axis). Thus, it becomes easy to secure a large number of rollers 50 and a large space for disposing the rollers 50 in the circumferential direction of the pulley 17. That is, the roller 5 around the axis
It becomes easy to make the mass distribution of 0 non-uniform.

(11) The corresponding rotation order component of the roller 50 arranged on the bottom dead center side around the axis of the rotation shaft 16 is higher than the corresponding rotation order component of the roller 50 arranged on the top dead center side. It is set next. In the present embodiment, this is realized by setting the distance R ₃ with respect to the roller 50 on the bottom dead center side around the axis line to be larger than the distance R _{2 with} respect to the roller 50 on the top dead center side. Therefore, with respect to the rollers 50 on the bottom dead center side around the axis, it becomes easy to secure a large number of rollers 50 and a large number of spaces in the circumferential direction of the pulley 17. That is, setting the corresponding rotation order component of the roller 50 on the bottom dead center side around the axis higher than the corresponding rotation order component of the roller 50 on the top dead center means setting the roller on the bottom dead center side. It is suitable to make the mass distribution of 50 larger than that at the top dead center side.

The embodiment is not limited to the above, and the following modes may be adopted, for example. In the pulley 17, if the mass distribution of the rollers (mass bodies) on the bottom dead center side around the axis of the rotating shaft 16 is set to be larger than that on the top dead center side, the corresponding rollers on the bottom dead center side correspond. The rotation order component may be set to a lower order than the corresponding rotation order component of the roller on the top dead center side.

In the pulley 17, if the mass distribution of the rollers (mass bodies) on the bottom dead center side around the axis of the rotary shaft 16 is set to be larger than that on the top dead center side, the rollers on the bottom dead center side are set. The mass of each of the rollers may be set smaller than the mass of each of the rollers on the top dead center side.

In the pulley 17, if the mass distribution of the roller (mass body) on the bottom dead center side around the axis of the rotary shaft 16 is set to be larger than that on the top dead center side, the roller on the bottom dead center side is set. May be set smaller than the number of the rollers on the top dead center side.

In the above embodiment, the axial length of a part of the plurality of rollers (47, 50) may be different from that of the other. According to this, due to the difference in the length, it is possible to make the mass of one of a part of the plurality of rollers (47, 50) different from that of the other. Therefore, due to this difference in mass, it becomes possible to cancel the bias of the conversion mechanism around the axis of the rotary shaft 16. According to this configuration, for example, even if the rollers (47, 50) having the same diameter are set, the masses of the rollers (47, 50) can be different from each other. In this case, for example, the configuration is as shown in FIG. In the configuration of FIG. 7, the number of rollers 47 and a part of the rollers 47 in the axial direction are changed in the first embodiment. That is, in this configuration, the rollers 47 are housed in all the recesses 45. Also, the recesses 45D, 45E, 4
The axial length of the 5F of the roller 47 (and L ₂₎
Is set longer than the axial length (L ₁ ) of the roller 47 of the recesses 45A, 45B, 45C.
The diameters of all the rollers 47 are set equal (to d ₁ ). As a result, the mass distribution of the rollers 47 in the pulley 17 is set to be larger on the bottom dead center side than on the top dead center side around the axis of the rotating shaft 16.

In the above embodiment, a material of a part of the plurality of rollers (47, 50) may have a density different from that of the other materials. According to this, due to the difference in the material, the mass of one of the plurality of rollers (47, 50) can be different from that of the other. Therefore, due to this difference in mass, it becomes possible to cancel the bias of the conversion mechanism around the axis of the rotary shaft 16. According to this configuration, for example, even the rollers (47, 50) having the same shape and the same size can have different masses.

In the above embodiment, the rollers 47, 5
0 may be formed by using copper, tungsten, or the like. In the above embodiment, the pulley body 42 may be made of metal.

The mass distribution of the pulley body 42 around the axis of the rotary shaft 16 may be adjusted by changing the shape of the lightening portion in the periphery of the recess 45 and the like in the pulley body 42.

In the above embodiment, the mass body may be formed in a spherical shape. In the above embodiment, the recess 45 formed in the pulley 17
The pendulum motion is performed by the rollers 47 and 50 rolling along the rolling guide surface 46 of the above. On the contrary,
The pulley may be provided with a mass body that performs a pendulum motion with a support shaft fixed to the pulley as a fulcrum. Further, a supporting shaft may be provided on the mass body itself, and the supporting shaft may be inserted into a hole formed in the pulley to support the mass body on the pulley so as to allow pendulum movement.

In the above embodiment, a plurality of mass bodies are provided in the rotating body, but it is also possible to provide only one mass body. In this case, in the compressor, this one mass body is provided so as to cancel the bias of the conversion mechanism around the axis of the rotation shaft.

In the above embodiment, the mass body and the like are provided so as to correspond to one or two rotational order components, but it may be configured to correspond to three or more rotational order components.

In the above embodiment, the value of the ratio R / r is set so as to correspond to the rotational order component in the rotational vibration generated by the compressor C, but the present invention is not limited to this. For example, in order to cope with the rotational order component in the rotational vibration generated by the vehicle engine E and auxiliary machinery (rotating machine such as oil pump for power steering) operatively connected to the compressor C by a power transmission member such as the belt 18. The value of the ratio R / r may be set.

In the compressor C, a positioning means for assembling the pulley 17 and the rotary shaft 16 in the circumferential direction of the rotary shaft 16 may be provided. According to this, the work efficiency when assembling the pulley 17 to the rotating shaft 16 is improved.

The number of the cylinder bores 24 of the compressor C may be set to any number. Generally, as a compressor used in a vehicle air conditioner, the number of cylinder bores 24 is often set to any of 3 to 7. Further, when the number of the cylinder bores 24 is set to 3, the torque fluctuation amount of the rotational vibration of the rotary shaft 16 is likely to be larger than when the number of the cylinder bores 24 is set to 4 or more. That is, in the compressor in which the number of the cylinder bores 24 is set to 3, the rotational vibration suppressing action of the mass body is particularly useful.

The pulley 17 is not a single-sided compressor that causes a single-headed piston to perform a compression operation like the compressor C, but a double-headed type in the cylinder bores provided on both front and rear sides of the crank chamber. It may be provided in a two-sided compressor that causes the piston to perform a compression operation.

The compressor C is replaced by a cam plate (swash plate 2
0) may rotate integrally with the rotary shaft 16, and may be of a type in which a cam plate is supported so as to be rotatable relative to the rotary shaft and swings, for example, a wobble type compressor.

In all the above-mentioned embodiments, the application examples of the piston type compressor in which the piston reciprocates are shown.
It may be applied to a rotary compressor such as a scroll compressor. In the above embodiment, as the rotating body, a sprocket, a gear, or the like may be applied instead of the pulley.

The rotating body may be applied to a rotating member housed in the housing of the compressor C. For example, the mass body may be provided in the rotary support 19 or other specially provided member that is operatively connected to the rotary shaft 16 in the housing to suppress the rotational vibration of the rotary shaft 16.

In all of the above-described embodiments, the central axis of the pendulum motion of the mass body does not necessarily have to be parallel to the central axis of rotation of the rotating body on which the mass body is provided. In this case, the central axis of the pendulum motion may be inclined with respect to the central axis of rotation of the rotating body within a range where a desired effect can be obtained in suppressing the transmission torque fluctuation. In the state where the central axis of the pendulum motion is inclined with respect to the central axis of rotation of the rotating body, for example, the distance Rs described below is defined as the distance between the center of the pendulum motion and the central axis of rotation of the rotating body. I decided to. That is, the distance between the intersection of the center axis of the pendulum movement and the plane orthogonal to the center axis of the pendulum movement and passing through the center of gravity of the mass body, and the distance between the rotation center axis of the rotor body and the distance Rs.

[0115]

As described in detail above, according to the invention described in claims 1 to 12, in the compressor, it is possible to reduce the rotational vibration and the vibration due to the bias of the conversion mechanism around the axis of the rotating shaft. In addition to being possible, it is possible to reduce the size and weight.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view showing an outline of a compressor according to a first embodiment.

2A is a schematic front view showing the outline of the pulley, and FIG. 2B is a schematic partial sectional view taken along the line bb of FIG. 2A.

FIG. 3 is a schematic front view showing an outline of a pulley according to a second embodiment.

FIG. 4 is a schematic front view showing the outline of a pulley according to a third embodiment.

FIG. 5 is a schematic front view showing the outline of a pulley according to a fourth embodiment.

FIG. 6 is a schematic front view showing the outline of a pulley according to a fifth embodiment.

7A is a schematic front view showing an outline of a pulley of another example, and FIG. 7B is a schematic partial sectional view taken along line bb of FIG. 7A.

[Explanation of symbols]

16 ... Rotating shaft, 17 ... Pulley as rotating body, 19 ... Rotating support body, 20 ... Swash plate, 21 ... Hinge mechanism, 25 ... Piston as compression member, 26 ... Shoe (19, 20, 2)
1 and 26 form a conversion mechanism, and the conversion mechanism, 16 and 25 form a piston type compression mechanism), 46 ... Rolling guide surfaces as guide surfaces, 47, 50 ... Rolls as mass bodies, C ... Compressor.

Continued front page    (72) Inventor Takayasu Suzuki             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Akinori Kanai             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Taku Yasaya             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries F term (reference) 3H076 AA06 BB01 BB38 CC12 CC16                       CC20 CC40

Claims (12)

[Claims] 1. A conversion mechanism for converting the rotational movement of a rotary shaft into a compression movement of a compression member in a compression mechanism, a rotary body integrally rotatable with the rotary shaft, and a rotary body provided on the rotary body. A compressor provided with a mass body that passes through a point separated from the rotation center axis of the rotating body by a predetermined distance and performs a pendulum motion about an axis substantially parallel to the rotation center axis. A compressor characterized in that the mass body is provided so as to cancel the unbalanced weight of the conversion mechanism around the axis of the rotating shaft. 2. The compressor according to claim 1, wherein a plurality of the mass bodies are provided and are arranged at non-uniform intervals in the circumferential direction of the rotating body. 3. The compressor according to claim 1, wherein a plurality of the mass bodies are provided, and one of the mass bodies has a mass different from other mass bodies. 4. The compressor according to claim 3, wherein a part of the mass body has a volume different from that of the other mass bodies. 5. The mass body is a cylindrical roller arranged movably along a guide surface having an arcuate cross section formed on the rotating body, and a part of the mass body is The compressor according to claim 4, wherein its diameter is different from that of the other mass bodies. 6. The mass body is a cylindrical roller movably arranged along a guide surface having an arcuate cross section formed on the rotating body, and a part of the mass body is The compressor according to claim 4 or 5, wherein its axial length is different from that of the other mass bodies. 7. The compressor according to claim 3, wherein a part of the mass body is made of a material having a density different from that of the other mass bodies. 8. A plurality of the mass bodies are provided, and a part of the mass bodies is different from the other mass bodies in a distance between a pendulum motion center thereof and a rotation center axis line of the rotating body. The compressor according to any one of claims 1 to 7. 9. The compression mechanism is a piston type compression mechanism including a plurality of pistons as the compression member around the axis of the rotation shaft, and the conversion mechanism is fixed so as to be integrally rotatable with respect to the rotation shaft. A rotary support, a swash plate integrally rotatably connected to the rotary support via a hinge mechanism provided on the top dead center side around the axis of the rotary shaft, the piston and the swash plate. A shoe interposed therebetween, the swash plate is supported by the hinge mechanism so as to be tiltable with respect to the axial direction of the rotation shaft, and the mass body is located at the bottom dead center side rather than the top dead center side. The compressor according to any one of claims 1 to 8, wherein the mass distribution is set to a large value. 10. The compressor according to claim 9, wherein a plurality of the mass bodies are provided, and the number of the rotating bodies on the bottom dead center side is set to be larger than that on the top dead center side. 11. A plurality of the mass bodies are provided, and a mass of one of the mass bodies arranged on the bottom dead center side is equal to one mass of the mass body arranged on the top dead center side. The weight is set to be larger than the mass.
Or the compressor according to 10. 12. A plurality of mass bodies are provided, and a corresponding rotation order component of the mass body arranged on the bottom dead center side corresponds to the mass body arranged on the top dead center side. The compressor according to any one of claims 9 to 11, which is set to a higher order than a rotation order component.